Five spindle fluting machine

ABSTRACT

A new machine for and method of manufacturing fluted pin fasteners and the pins produced thereby are disclosed which utilize a circular grinding arrangement of a plurality of grinders which grind flutes into a threaded pin. An internally threaded collar threads onto the pin. When the collar engages a surface of a work piece, resistance to further threading increases. When sufficient resistance to threading occurs, the driver deforms the lobes of the collar radially inward toward the axis of the collar. Material of the collar positioned internally from the lobes responds to deformation of the lobes and flows radially inward into the flutes of the pin to lock the collar, pin, and work piece together. The driver then rotates freely, and a joint has been made with a predetermined axial load thereby locking the component parts together. The apparatus grinding the flutes into the pins comprises a vibratory feed bowl loading threaded pins into a four station rotary drum assembly rotationally driven by a drive mechanism through a plurality of stations. There is a feed station to receive pins into drum assembly, a grind station to grind the pins, and an eject station to eject the ground pins. The circular arrangement of grinders is mounted on a table which is translated up and down by an air spring against a cam wheel to grind the pins located at the grinding station.

This application is a division of patent application Ser. No. 08/951,925filed Oct. 16, 1997, now U.S. Pat. No. 5,906,537 which is a division ofpatent application No. 08/536,647 filed Sep. 29, 1995, now U.S. Pat. No.5,716, 280.

BACKGROUND OF THE INVENTION

This invention relates to fasteners, methods of manufacturing fasteners,and apparatuses used to manufacture fasteners.

The venerable threaded fasteners consist of a nut and a bolt. The nuthas internal threads that thread onto external threads of the bolt.Surfaces of the nut and bolt are formed to receive wrenches which areoperated to tightly join the fastener members and one or more piecestogether. Broadly, another name for a bolt is a threaded pin, andanother name for a nut is a collar.

Many environments in which fasteners are used require the fasteners tohave extremely high integrity and strength. Fasteners must bear loadsboth along a longitudinal axis and radially on the axis. Moreparticularly, when fasteners join together two or more sheets and thesheets are loaded in their planes with different loads, one sheet tendsto slide relative to the other. Fasteners passing through both sheetsbecome loaded in shear to prevent the sheets from sliding relative toeach other. Axial loads arise from clamping sheets between a head of thepin on one side of the sheets and the collar on the other side of thesheets.

Frequently, fasteners are required to function well in environmentswhere they are cyclically stressed under conditions that could give riseto fatigue failure. A fastener holding two sheets together with anacceptable axial load resists fatigue failure.

An obviously desirable feature of a fasteners is that it does notloosen, fail, or otherwise come apart in service. Many different deviceshave been used to keep collars and pins together. One way of locking thecollar and pin is to deform the threads of the collar so that they bearin radial compression against the threads of the pin. In this method,the resistance to unthreading is purely frictional. The threads arecommonly deformed at a manufacturing facility in preference to thefield, but field deformation has also been practiced.

It is also highly desirable to know and control the axial load that thefastener is subject to when holding the sheet together. The axial loadcorrelates to the resistance of a collar to further threading onto apin. As the resistance to further threading increases, the axial loadincreases, and the torque required to turn the collar increases. Theserelationships have been used in developed fasteners to providepredetermined axial loads.

In one prior art fastener, a section of a collar adapted to receive awrench is attached to the main part of the collar by a frangible breakneck that breaks upon the application of a predetermined torquecorresponding to the desired axial load. The features of a deformedthread lock and a collar with a frangible break neck for axial loadcontrol have been combined in one collar. Regrettably, the combinationhas shortcomings. A thread lock obtained by deformation of the collarthreads to form a thread lock, is performed at the factory or in thefield before the collar is threaded onto the pin. Thus, the collar doesnot freely thread onto the pin. This makes threading the collar onto thepin somewhat difficult. Protective and lubricative coatings applied tothe threads of the collar to aid threading can be worn off of a collarhaving this type of thread lock by considerable frictional drag betweenthe threads of the collar and pin. Where corrosion control is important,a circular band of bare metal on the collar is created by failure of thebreak neck. This band is not protected by corrosion inhibitors appliedto the fastener when it was manufactured.

Further, the separation of the collar into two pieces presents severalproblems. The fact that the section adapted to receive the wrenchseparates from the threaded section of the collar creates a spare piecethat must be removed from the environment where the fastener isattached. This type of fastener is also comparatively expensive becauseit is difficult to manufacture and requires considerable machining inits formation. The frangible break neck section needs to have very closedimensional tolerances if small variations in break off torques arerequired. This problem is compounded by machine tool wear in the toolsthat make the part and also because the break neck section becomeselliptically shaped after the collar threads are deformed to incorporatethe thread locking feature into the fastener. Also, the frictional dragbetween the shear pin and the collar in a fastener system employing apre-existing deformed thread lock results in a broad range of axial pinloads. The broad range of loads occurs because the drag created by thedeformed threads varies greatly among fasteners and is a significantcomponent in the resistance that effects the failure of the frangiblebreak neck. Therefore, the axial load created by the set amount oftorque at which the frangible break neck fails varies greatly because ofthe difficulty in controlling the exact amount of the resistance betweenthe deformed collar and the pin.

A second approach to a locking system employs a pin having an outergroove adapted to receive a deformed collar material. The collar isthreaded onto the pin to develop desired axial load, and is thendeformed radially inward into the groove so that the deformed collarmaterial is restrained by the walls of the groove and establishesinterference. The groove can be made longitudinally or annularly. In onetype of such fastener a collar is threaded onto a pin with one settingtool. A second setting tool radially deforms the collar into threads ofthe pin to effect the interference lock.

To solve these problems, U.S. Patent Nos. 4,260,005, 4,383,353, and4,544,312 all to Stencel, the disclosures of which are fullyincorporated herein by reference, disclose an improved collar and pin.The collar has external lobes capable of deformation. The deformation ofthe lobes displaces collar material into an axial bore of the collar, sothat the displaced material is brought into interference with a surfaceof the pin to produce a rotational lock.

The pin has a longitudinally extending shank attached to a head and aplurality of short rounded grooves or flutes extending longitudinallyalong the shank. Each flute is concave outward in cross section. At theend of the shank opposite the head, roll formed threads cross over theflutes to receive the internal threads of the collar. While beingthreaded onto the pin, the longitudinally extending lobes on the outersurface of the collar act as a wrenching surface to which a tighteningtangential load is applied. Once a determined tangential load or torqueis applied, the lobes fail plastically in radial compression. When thelobes plastically deform, material located inwardly from the lobesplastically displaces into the flutes establishing a lockingrelationship between the collar and the pin created by the interferingmaterial.

To form the pin, the shank of the pin is given a preformed configurationsuch as that of a generally regular polygon, specifically hexagonal orpentagonal. The corners between the flat sides are rounded. The shank ofthe pin is then roll formed to introduce threads onto the shank whichintersect the flat sides of the shank. The roll forming process deformsmaterial to form the flutes from the flats. The crests of the flutes areformed by radially outwardly displaced shank material formed during theroll forming.

On the collar, each lobe has a convex curvature in radial planes, andthe curvatures of the lobes are equal to each other. To make it easy toinstall a driver onto the collar for tightening, it is preferred thatthe lobes be located at equally angular distances from each other forexample, 120° apart. A driver bears against the lobes with a tangentialcomponent force and a component of force in the direction of the axis ofthe collar.

The collar threads freely onto the work piece of the pin until thecollar engages the work piece. Thereupon resistance builds up until thelobes fail inwardly under radial compression. Failure occurs in just afew degrees of arc, and therefore, the amount of axial load on thestructure being fastened is determined accurately with small variations.With the failure of the lobes, the setting driver turns freely on thecollar indicating that the fastener system is set. Thus, the axial loadis controlled without throw-away pieces. Corrosion inhibitors andlubricants are not affected by this deformation.

Though the fasteners of the above patents are made relativelyinexpensively, the production of the pins for these fasteners hasencountered some inefficiencies. The preforming of the pin shank is arelatively expensive process requiring the fabrication of a cylindricalpin shape and the milling of the desired number of flats onto an end ofthe pin shank. The precision milling process, which is necessary toproduce the preformed pins, is both labor and time intensive. Thisincreases the cost of the pins. After the flats are formed onto the pin,the pin is thread rolled to introduce the threads onto the pin. Theflats tend to cause the pins to wobble and otherwise rotate irregularlybetween the thread rolling dies used in the roll forming process. Theirregular rotation of the pins in the dies results in a relatively highscrap rate and increased cost for the pins.

Thus, reduction in the required labor and time for fabricating the pinsis desirable to increase the production rate and reduce the productioncost of the pins. It is also desirable to reduce the amount of scrapproduced during the roll forming process thereby decreasing the cost ofproducing the pins.

BRIEF SUMMARY OF THE INVENTION

There is, therefore, provided in the practice of this invention a novelmethod for fabricating self locking fasteners providing set axial loads.The method comprises fabricating a pin and grinding at least one fluteon the pin.

In a preferred embodiment of the method, the pin is lubricated andinserted at a feed station into a hold down assembly of a drum assemblywherein it is held between a hold down and an insert blank of the holddown assembly. The drum assembly is then rotated until the hold downassembly is at a grind station and a second hold down assembly is at thefeed station. The drum assembly is then temporarily stopped while asecond pin is inserted into the second hold down assembly and held bythe hold down assembly and the pin is translated into a grindingposition. While the pin is in the grinding position, a grinding assemblyis cycled up and down past the pin grinding the flutes on the pin. Thepin is then translated up out of the grinding position. The drumassembly is again rotated until the hold down assembly is at an ejectstation, the second hold down assembly is at the grind station, and athird hold down assembly is at the feed station. The rotation of thedrum assembly is again temporarily stopped while the pin is releasedfrom and falls out of the hold down assembly, the second pin is ground,and a third pin is inserted into the third hold down assembly. Afterthese operations are complete, the drum assembly is again rotated untila fourth hold down assembly is at the feed station, the hold downassembly is at an idle station, the second hold down assembly is at theeject station, and the third hold down assembly is at the grind station.The rotation of the drum assembly is again temporarily stopped while thesame operations are performed on the pins. If the pin does not fall outof the hold down assembly at the eject station, an eject arm is actuatedby the rotation of the drum assembly and forces the pin out of the holddown assembly. These operations are performed substantiallysimultaneously. Further, the operations are continuously repeated tomass produce the pins.

Also provided in the practice of this invention is a novel machine forfluting threaded pin blanks. The machine comprises a hold down assemblywhich holds the pin while a circular grinding arrangement grinds thepin.

In a preferred embodiment of the machine, a rotary drum assembly havinga plurality of hold down assemblies rotates through four stations. Afeed track guides the threaded pin blanks past a lubricating mechanismand into a hold down assembly position at a feed station. A grindingassembly grinds the threaded pin blanks held by the hold down assembliesat a grind station. An eject arm assures that the fluted pins areejected at the eject station. The pin is held between a hold down and aninsert blank of the hold down assembly. The hold down is translated upand down to clamp and release the pin by a hold down cam followerattached to the hold down. The hold down cam follower follows a railcam. At the grind station the entire hold down assembly is pushed downinto a grinding position by a push down lever. Both the push down leverand the grinding assembly are controlled by a single cam assembly havingtwo cam wheels. The grinding assembly comprises five grinders arrangedin a circular pattern. Multiple means for adjusting the grinders areprovided. Rotation is imported to the drum assembly and the cam assemblyby a drive mechanism.

There is further provided in the practice of this invention a novelgrinding assembly comprising a circular grinding arrangement. In apreferred embodiment, the circular grinding arrangement has at leastfive grinders. The center of the circular grinding arrangement isadjustable, and the diameter of the circular grinding arrangement isalso adjustable. The angles of the grinders which control the diameterof the circular arrangement may be adjusted individually orsimultaneously. Further, each grinder can be tilted up out of theassembly for maintenance.

There is still further provided in the practice of this invention anovel rotary drum assembly comprising a plurality of hold downassemblies and means for rotating the drum assembly so that the holddown assemblies rotate through a plurality of stations where operationsare performed on pins held by the hold down assemblies.

In a preferred embodiment of the rotary drum assembly, each hold downassembly comprises an insert blank with an aperture for receiving thepins or other work piece and a hold down slidable relative to the insertblank. The hold down is biased in a down position so that it clamps apin by a hold down compression spring. The hold down is forced torelease the head of the pin by a follower following a rail cam. Eachhold down assembly is translated in its entirety into a grindingposition by a push down lever actuated by a push down cam wheel. Thehold down assemblies are biased in the up position by a hold downassembly compression spring. The means for rotating the drum assemblycomprises a drive mechanism utilizing an indexer to rotate the drumassembly and pause the drum assembly when the hold down assembly arepositioned at the stations. The drum also comprises an outer shell whichaids in loading pins into the hold down assemblies.

Also provided in the practice of this invention is a novel pin fastenerhaving a plurality of flutes fabricated by threading the pin andgrinding the flutes on the pin.

These and other features and advantages of the present invention willappear from the following Detailed Description and the accompanyingdrawings in which similar reference characters denote similar elementsthroughout the several views.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic grind side view of a five spindle fluting machineaccording to the present invention which has been simplified forclarity;

FIG. 2 is a top view of the five spindle fluting machine of FIG. 1;

FIG. 3 is a partial ejection side view in partial cross section of thefive spindle fluting machine of FIG. 1 illustrating a grinding assembly,cam assembly, and drum assembly;

FIG. 4 is a feed side partial cross-sectional view of the drum assemblyof the five spindle fluting machine of FIG. 1 illustrating the feedstation and lubricating mechanism;

FIG. 5 is an illustration of how a pin is positioned in an insert blank;

FIG. 6 is an ejection side view in partial cross-section of the drumassembly of FIG. 4 with portions of an outer shell of the drum assemblyremoved;

FIG. 7 is a partial cross-sectional top view of the drum assembly ofFIG. 4 illustrating a rail cam and hold down assembly followers actuatedby the rail cam;

FIG. 8 is a partial cross-sectional view of the bottom of the drumassembly of FIG. 4 illustrating the feed track and the ejection arm;

FIG. 9 is a partial cross-sectional view of the drum assembly of FIG. 4taken along line 9--9 in FIG. 8;

FIG. 10 is a partial cross-sectional view of the drum assembly shown inFIG. 4 taken along line 10--10 of FIG. 8;

FIG. 11 is an idle side view of the cam assembly;

FIG. 12 is an ejection side view of the cam assembly;

FIG. 13 is a grind side view of the cam assembly;

FIG. 14 is a schematic top down view with detail removed for clarityillustrating a grinder assembly typical of all the grinder assembliesand a mounting plate of the grinding assembly of FIG. 3.

FIG. 15 is a partial side view of the grinding assembly shown in FIG. 14illustrating an individual pivot base adjustment mechanism;

FIG. 16 is a partial side view of the grinding assembly shown in FIG. 14illustrating a locking screw for fixing the adjustment made by theindividual pivot base adjustment mechanism illustrated in FIG. 15;

FIG. 17 is a partial cross-sectional top view of a grinder adjustmentmechanism for the grinder taken from within circle 17 of FIG. 14;

FIG. 18 is a side view of the adjustment mechanism of FIG. 17;

FIG. 19 is a side view of the grinder assembly shown in FIG. 14illustrating methods for adjusting the position of the grinder;

FIG. 20 is a cross-sectional view of the grinder assembly of FIG. 14taken along line 20--20 of FIG. 19;

FIG. 21 is an enlarged cross-sectional view of a pin fabricated by thefive spindle fluting machine of FIG. 1 illustrating flute run out; and

FIG. 22 is an exploded view of a fastener having a pin fabricatedaccording to the present invention just before the collar is threadedonto the pin to complete the fastener.

DETAILED DESCRIPTION

I. Overview

FIGS. 1 and 2 show a five spindle fluting machine according the presentinvention. The machine comprises a vibratory feed bowl 20 and feed bowlcontrol 21. The feed bowl is adjustably mounted to a support frame 22. Afeed track 24, stabilized and supported by a track support 26, extendsfrom the feed bowl. A screw assembly 28 is provided to adjust the heightof the track and feed bowl relative to the remainder of the machine. Thefeed track extends downwardly from the feed bowl at an angle andterminates at a generally circular rotary drum assembly, generallydesignated 30. The feed bowl orientates the threaded pin blanks loadedtherein and transfers them to the feed track. The drum assembly receivesthe threaded pin blanks from the feed track at a feed station. The screwassembly 28 is used to adjust the height at which the feed trackintroduces the pins into the drum assembly assuring consistentplacement. After the drum assembly has received a pin, a drivemechanism, generally designated 32, rotates the drum assembly until thepin is at a grind station. A grinding assembly, generally designated 34,which is actuated by a cam assembly 124 (FIG. 3), grinds the flutes ontothe pin. The drive mechanism then rotates the drum assembly until thepin is at an eject station from which the fluted pin is ejected into achute 36. The chute guides the fluted pin to a collection pan 38removably mounted to the frame on the opposite side of the machine fromthe feed bowl.

II Drum Assembly

Referring to FIG. 3, the preferred embodiment shown of the rotary drumassembly 30 has four equally spaced rotating hold down assemblies,generally designated 39, which are repeatedly rotated through fourstations. More or fewer hold down assemblies and stations could be useddepending on the number of operations required or the desired productionrate, and the number of hold down assemblies is not required to equalthe number of stations. The hold down assemblies are spaced so that theyare simultaneously at a separate station. When the hold down assembliesare positioned at the stations, the rotation of the drum assembly istemporarily stopped, so that the stations can perform their operations.After the operations are complete, the drum assembly is again rotateduntil the hold down assemblies are positioned at the next stations.Viewing the machine from the eject side shown in FIG. 3, three of thestations are visible: the eject station 40, the grind station 42, andthe idle station 44. The fourth station, shown in FIG. 4, is the feedstation 46, which is on the opposite side of the drum from the ejectstation. The drum rotates in a direction so that, starting with the feedstation, a hold down assembly is first presented to the feed station,second to the grind station, third to the eject station, and fourth tothe idle station. After the idle station, the hold down assembly isagain presented to the feed station, and the pattern is started overagain and continuously repeated.

A. Hold Down Assembly

Referring to FIG. 4, each hold down assembly 39 comprises an insertblank 48 for receiving pins and a hold down 50 to clamp and hold thepins in the insert blank. The hold down fits through an elongated slot52 centrally located in the insert blank. The slot is longer than theportion of the hold down that is contained inside the slot, so that thehold down can move up and down within the slot. The lower end of theinsert blank, shown in detail in FIG. 5, has a flange 53 protrudingradially outward from the drum that defines an aperture 54 for receivingpins 55 from the feed track 24. A counter sink 57 is formed around theaperture which allows the insert blank to receive pins having differenttypes of heads 59. When the diameter D of the pin changes, the insertblank must be changed, and a different size insert blank is required foreach pin diameter. The apertures of the insert blanks are sized so thatthe distance L from the back 56 of the insert blank to the outer edge 58of the pin is always the same. This requires re-centering of thegrinding assembly when the pin diameter is changed, but it prevents thepins from protruding too far out of the drum assembly and contactingstationary parts which could interfere with the operation of themachine. Further, positioning the pin in this manner keeps the head ofthe pin centered under the hold down thereby preventing the pin fromfalling out of the hold down assembly.

Referring to FIGS. 6, 7, and 8, a tip 80 at the lower end of the holddown 50 engages the top of the pin to hold it in the aperture of theinsert blank. The hold down assembly at the grind station 42 of FIG. 6illustrates the down position of the hold down. A schematically shownhold down compression spring 82 (also FIG. 9) biases the hold downtoward the down position thereby holding the pin by the head with acompression force between the insert blank flange and the hold down tip.The hold down spring 82 is held in compression between a top plate 83,which is fixed relative to the insert blank 48 and the spring engagementportion 85 of the hold down 50. Thus, the hold down can move within theslot 52 of the insert blank, and the hold down spring 82 biases ittoward a down position shown in FIG. 6 at the grind station 42.

B. Rail Cam and Hold Down Assembly Followers

To allow pins to feed into the hold down assembly at the feed stationand eject from the hold down assembly at the eject station, each holddown assembly further comprises a follower 84 having a roller 86 whichrolls across a rail cam 88. Each follower 84 is connected to a slidingpin 90 passing through the top section 93 of the drum assembly. Thesliding pin has a slot 92 at its lower end for receiving a flange 94 onthe top of the hold down (also FIG. 9).

The generally circular rail cam functions to lift the followers, slidepins, and hold downs overcoming the force of the hold down spring 82, sothat the hold down does not obstruct the placement of pins into andremoval of pins out of the insert blanks. As the drum assembly isrotated by the drive mechanism in the direction shown by arrow 96, thefollowers move through four (4) regions of the rail cam. The majority ofthe rail cam is comprised by the lifted region 98, which corresponds tothe eject, idle, and feed stations. When the follower is in the liftedregion, the hold down is lifted up into an opening 99 of the top section93. When the hold down is lifted up, a gap 100 is left between the holddown tip and the insert blank to allow for insertion and ejection of thepin. Following the rotation of the follower, the downward transitionregion 102 of the rail cam is next. The downward region extends fromjust after the feed station to just before the grind station 42. Thus,the roller rolls downward on the rail cam until the hold down tip 80engages the head of the pin 55. Then the follower rotates through theopen region 104 of the discontinuous rail cam. This region correspondsto the grind station. Thus, during grinding, the force of the hold downspring holds the pin tightly between the hold down tip and the insertblank. The fourth region is the upward transition region 106. The loweredge 107 of the upward region is below the horizontal position of theroller, so that the roller smoothly engages the upward region. When theroller engages this region, the follower and hold down are pulled upwardto release the pin for ejection. The remainder of the features andcomponents of the drum assembly will be discussed in the context of theoperations of the four stations and the drive mechanism.

C. Feed Station

Referring back to FIG. 4, the operation of each station will now bediscussed starting with the feed station. At the feed station of thedrum assembly, a lubrication mechanism, generally designated 60,lubricates the pin prior to insertion into the hold down assembly. Thelubrication mechanism comprises a lubricant applicator 62 with twonozzles 64 positioned on opposite sides of the applicator with the pin55 therebetween. A lubricant supply line 66 and an air supply line 68extend through the applicator to the nozzles. In each nozzle, the tips69 of the air line are located farther away from the nozzle opening 70than the tips 71 of the oil line. While the pin is still in the feedtrack 24, shown in phantom cross section, an oil cam follower 72, whichis connected to a grinding follower 146 (FIG. 3) to be discussed later,is actuated by the grinding follower causing a lubricant controlmechanism 74 to inject a drop of lubricant into the nozzle. Thelubricant used, which is typically an oil, varies dependent on manyfactors including the material from which the pin is fabricated.Immediately following the injection of the lubricant, the controlmechanisms shoots a burst of air out of the nozzle opening. Thus, thelubricant is carried by the air and sprayed onto the pin in a pattern76, shown in phantom, covering the end of the pin with lubricant. Thepattern is controlled by the angles of the internal walls 78 of thenozzle and the size of the nozzle opening 70. Referring to FIG. 8 inaddition to FIG. 4, the feed track 24 abuts the drum assembly. The nextpin 51 to be loaded into the hold down assembly at the feed station isloaded in one of at least two ways.

The feed track is provided with a timed escapement 79, shownschematically in FIG. 1. The escapement releases a pin when the drumassembly is properly aligned to receive a pin from the feed track intothe hold down assembly. Preferably, an outer shell or skirt 81 enclosesthe drum assembly negating the need for an escapement. The next pins 51(FIG. 8) to be loaded into the drum assembly rest against and slide overthe shell until the opening of the hold down assembly is presented tothe feed track. The shell also prevents pins from becoming lodged in thedrum assembly which could damage the drum assembly by obstructing itsrotation. The shell 81 is broken into four segments which correspond tothe hold down assemblies and are translated up and down as part of thehold down assemblies.

Because the feed track is angled downward, gravity moves the pins alongthe feed track and transfers them from the feed track to the drumassembly. The drum assembly is placed at an angle with the verticaldirection, so that the axis of the drum assembly, which corresponds to adrum shaft 157, is perpendicular to the longitudinal axis of the feedtrack. Thus, the longitudinal axis of the pins are parallel to the axisof the drum assembly simplifying their insertion into the insert blanks.The angled drum assembly is also advantageous because the hold down doesnot engage the head of the pin until the hold down follower has rotatedat least partially through the downward transition region. The angle ofthe drum assembly utilizes gravity to hold the pin in the insert blankuntil the hold down engages the pin. This is accomplished by orientingthe drum assembly so the feed station is the highest station on the drumassembly making the flange 53 of the insert blank angled upward at thefeed station (FIG. 1). An additional component (not shown) has beenadded to prevent the pin from falling out of the insert blank assuringthat the pin stays in the insert blank until the hold down engages thepin. The additional component is desirable to allow the drum assembly torotate at higher rates without throwing the pins out of the hold downassembly.

D. Eject and Idle Stations

Referring to FIGS. 3 and 8, at the eject station another cam is utilizedto eject the pins from the insert blanks. The eject arm 108 has a camfollowing corner 110 which engages the lead alignment pins 112. The leadalignment pins and the following alignment pins 114 are pressure fittedinto the bottom plate 113 and are inserted into the top section 93 ofthe drum assembly. The lead alignment pins function both to align thedrum assembly and to actuate the eject arm. Thus, the lead alignmentpins function as cams. The eject arm is pivotally mounted on a T-supportmember 109 with a pivoting mechanism 111. The T-support member, whichalso mounts the rail cam 88, is attached to a cross support bar 115,which is fixed to the support frame 22. When the drum assembly isrotated, the corner of the eject arm engages the lead alignment pins 112forcing the eject arm outward as illustrated by arrow 117 therebypushing the pin 55 out of the insert blank. As discussed above, thetilted orientation of the drum assembly and gravity aid the feeding ofthe pins into the drum assembly. The ejection of the pins is also aidedby the tilted axis of the drum assembly. Referring temporarily back toFIG. 1 it can be seen that the eject station 40 is on the opposite sideof the feed station 46, and therefore, the eject station is the loweststation on the tilted drum assembly making the flange 53 of the insertblank 48 angled downward at the eject station. Thus, gravity pulls thepins downward out of the drum assembly.

The idle station is simply that, and therefore, no specific discussionis warranted. However, having an idle station allows for the addition ofanother operation.

E. Grind Station

Referring to FIGS. 9 and 10, the fourth and final station to discuss isthe grind station 42. As discussed above, the region of the rail camcorresponding to the grind station is the open region 104. This regionis open so that an entire hold down assembly of the drum positioned atthe grind station can be pushed downward to place the pin in a grindingposition shown in FIG. 9. The entire hold down assembly is free totranslate downward on the lead alignment pins 112 and the followingalignment pins 114 because the alignment pins are engaged by linearslide bearings 116 shown schematically in FIG. 10. A hold down assemblycompression spring 118 (shown schematically) biases the hold downassembly in the up position. The hold down compression spring iscontained by a spring holder 119 having a central opening 121 forreceiving the spring 118. A spring pin 123, which is press fit into thebottom plate 113 of the drum assembly, fits into the central opening 121of the spring holder and holds the spring in compression therein. Tomove the entire hold down assembly into the grinding position shown inFIG. 9, the force of the hold down assembly compression spring isovercome by a cam-actuated push down lever 120.

III. Cam Assembly

A push down cam wheel 122 which is part of the cam assembly, generallydesignated 124 and shown in FIG. 3, actuates the push down lever. FIGS.11-13 show a detail of the cam assembly 124. The push down lever 120engages the follower 84 of the hold down assembly positioned at thegrind station to push the hold down assembly into the grinding position.(FIG. 9) The push down lever is attached to a backing plate 126 which isattached at its other end to a push down follower 128 which follows thepush down cam wheel. The upper position of the push down lever is shownwith solid lines in FIG. 11, and the down position is shown in phantomlines. As the cam assembly shaft 130 rotates in bearings 131 held bysupport arms 132, 134, the push down cam wheel moves the push downfollower, and hence the push down lever, up and down. The push downlever in turn acts on the hold down follower to push the pin held by thehold down assembly into the grinding position.

The cam assembly is held to the support structure with the support arms132 and 134 which are attached to the cross support bar 115 shown inphantom in FIG. 12. The left support arm 132 extends through an aperture136 in the push down backing plate 126. A roller type bearing 140 (shownschematically), is attached to the push down backing plate 126 andslidably engages a track way 138 defined by the support arms. Thus, thebacking plate moves up and down relative to the support arms. The pushdown lever backing plate and follower are biased in the upper positionby push down tension spring 142. Thus, the push down tension springholds the push down cam follower against the push down cam wheel. Afterthe push down lever pushes the hold down assembly into the grindposition, the grinding assembly 34 is cycled up and down to grind thepin. The detail of the grinding assembly will be discussed below.However, it is advantageous to discuss the cycling of the grindingassembly at this point.

The cam assembly 124 also includes grinding cam wheel 144. Acorresponding grinding follower 146 is attached to an adjustment bracket148 which is attached with a flat bracket 150 to the grinding assembly34. As the cam assembly shaft rotates, the grinding follower and thegrinding assembly to which it is indirectly attached are cycled up anddown past the pin thereby grinding the pin. The length of the grindingassembly's cycle is constant and corresponds to the change in diameterof the grinding cam. A flute length adjustment screw 240 threads throughan arm 242 of the adjustment bracket and engages an upper surface 244 ofthe grinding assembly normal to the length of the flute lengthadjustment screw. The flat bracket has slotted apertures 246 allowingthe grinding assembly to move relative to the cam follower. By threadingthe screw 240 farther into the arm 242, the gap 248 between the arm andthe grinding assembly is increased, and thus, the grinding assembly isfarther away from the cam follower and the pin in the grinding position.Therefore, when the grinding assembly is cycled to grind the pin, thepin is ground over a shorter portion of the grinding assembly's cyclelength, and the flutes are shorter. By threading the screw 240 fartherout of the arm 242, the gap 248 is decreased, and thus, the grindingassembly is closer to the pin in the grinding position when the cycle isstarted. Therefore, because the pin is ground over a greater portion ofthe cycle of the grinding assembly, threading the flute lengthadjustment screw out of the adjustment bracket arm lengthens the flutes.Referring temporarily to FIG. 2, a position sensing device 247 such as amicrometer with a dial indicator 249 senses the length between thegrinding assembly and any fixed point on the machine. The dial indicatoris calibrated to display the flute length. If pins having differentlengths are to be ground, the dial indicator must be recalibrated.

The grinding cam appears substantially circular because only a shortstroke is required to grind the pin. However, the grind cam has three(3) different arcs: a cycling down arc 175 defined by arc segment AC, agrinding arc 165 defined by arc segment AB, and a down position arc 167defined by arc segment BA. The arc segments are defined by the directionof rotation of the cams shown by arrow 169. The grinding and cyclingdown arcs have a smaller diameter than the down position arc 167, andwhen the grinding follower is following the grinding arc, the grindingassembly is translated upward thereby grinding the pin. When thegrinding follower is following the cycling down arc, the grindingassembly is translated downward. To this end, the grinding and cyclingarcs do not have constant diameters unlike the down position arc. As thegrind cam rotates, grinding arc segment CB contacts the grindingfollower 146 and translates the grinding assembly upward. Point C is thepoint having the smallest diameter and corresponds to the grindingassembly being in the highest position. The grinding arc segment CBchanges diameter gradually so that the grinding moves at a slower pacewhile moving upwardly. It is during upward movement that the grindingactually takes place. The cycling arc segment AC moves the grindingassembly downward to the down position. The arc segment AC is shorterthan segment CB so the segment AC changes diameter quickly relative tosegment CB, and the grinding assembly moves quickly downward. Thus thegrinding assembly is translated upward during actual material removal ata slower pace then it is translated downward. The grinding assembly canbe translated downwardly at a faster pace because it is not furthergrinding the pin. The grinding arc segment AB corresponds to a push downarc 171 of the push down cam.

The push down arc 171 defined by segment DE is a constant diameter andfunctions to push the hold down assembly downward placing the pin in thegrinding position. Because the respective cam followers are engaging thepush down arc and the grinding arc at the same time, the pin is pushedinto the grinding position the entire time that the grinding assembly ismoving upwardly to grind the pin. Arcs defined by segments EF and GDtranslate the hold down assembly into the down position (FIG. 9) andinto the up position (FIG. 6) respectively. These segments arecharacterized by high acceleration. The high acceleration translates thehold down assembly to the up and down positions quickly, so the drum canbe rotated with minimal pause at the stations. The cycling down arcsegment AC corresponds to the arc segment GD which translate the holddown assembly to the up position. Thus, the hold down assembly istranslated to the up position simultaneously with the cycling down ofthe grinding assembly. Arc segment ED corresponds generally to the downposition arc segment BA, so the hold down assembly is in the up positionwhen the grinding assembly is in the down position.

IV. Drive Mechanism

Referring to FIGS. 1 and 3, rotation in the direction of arrow 141 isimparted to the cam assembly shaft 130 by the drive mechanism 32. Thedrive mechanism includes a motor 152 which transmits rotation around anaxis to a first bevel gear 154 which rotates in an opening 155 (FIG. 11)of the support arm 132 and in the direction of arrow 143. The motor ofthe drive assembly has a corresponding controller 153 capable of turningthe motor on and off and controlling the speed of the motor and hencethe rate of production. The first bevel gear engages a horizontal bevelgear 156 which is fixed to the cam assembly shaft.

Referring additionally to FIG. 7, the drive mechanism is also therotational means for the drum assembly in the direction of arrow 96.However, the rotation of the drum assembly is not constant. The drivemechanism, therefore, utilizes an indexer 158 to hold the drum assemblystationary for short periods of time, so that the necessary operationsat the different stations can be performed. The indexer rotates the drumexactly one quarter rotation each time it indexes. The indexer transmitsrotation in the direction of arrow 96 from the motor to a drum driveshaft 157 passing centrally through the drum. At the bottom of the drumthe drum drive shaft has a downwardly increasing diameter region 161. Aboss 163 extending downward from the bottom plate 113 has an innerdiameter which increases in the downward direction. Thus, the collarengages the increased diameter region preventing the drum assembly fromsliding down the drum drive shaft. The upper part of the drum assemblyis rotationally fixed to the drum drive shaft with a set screw (notshown). Further, the drum drive shaft is in two pieces, so a colletassembly 151 is provided to connect the pieces of the drum drive shaft.The drive assembly also includes a torque tender 160 as a safetymechanism to prevent damage to the motor should the drum assembly or camassembly become obstructed and prevented from rotation.

V. Grinding Assembly

Referring again to FIG. 3, the grinding assembly is free to cycle up anddown on the support frame 22 inside of a track way 162 attached to thesupport frame. Linear bearings 164 (schematically shown) are attached tothe grinding assembly and slide in the trackway 162. Specifically, thebearings are attached to the bearing support 166 and adjustment bearingsupport 168 which are in turn attached to the grinding assembly baseplate 170. The drum drive shaft 157 extends through the drum and downinto the base plate 170 thereby aligning the drum with the base plate. Abearing 159 allows the base plate to slide over the drum drive shaft. Anair shaft 172 of an air cylinder 174 biases the entire grinding assemblyin the up position shown in FIG. 3. Thus, during operation, the grindingfollower is held against the grinding cam by the force exerted by theair cylinder on the base plate. The grinding cam 144, discussed above,causes the grinding assembly to cycle into the down position while thedrum is rotating, and when the drum is stopped the push down cam pushthe pin into the grinding position and the grinding cam cycles thegrinding assembly up and down to grind the pin.

Referring to FIG. 14, a grinder mounting plate 176 is mounted onto thetop of the base plate 170, and five grinder assemblies, generallydesignated 178, are mounted on the grinder mounting plate. Though fivegrinders are used in the preferred embodiment shown, more or fewergrinders can be provided. Each grinder assembly, all of which aresubstantially the same, comprises a pivot base 180 in which a grinder182 is adjustably mounted. The grinders are positioned so that thegrinding wheels 184 form a circular grinding arrangement, generallydesignated 185, around the pin 55. The inner most radial points 181 ofthe grinding wheels form a circle with a diameter smaller than thediameter of the pin. Thus, the grinding wheels grind away material toform the flutes. It is also true that the outer most radial points andthe centers of the grinding wheels define circles. Further, thelongitudinal axes 206 of the grinders are tangential to a circle.

The pivot bases are mounted to the mounting plate with frictional holddown towers 186, which when tightened, prevent the pivot bases frommoving relative to the mounting plate. The apertures 187 of the towersare enlarged to allow the pivot bases to adjust relative to the mountingplate. (FIG. 20) The grinders are pneumatically powered and rotate atapproximately 40,000 rpm. The grinders are supplied with air by airhoses 188.

A. Grinding Assembly Adjustments

Because precise positioning of the grinding assembly is necessary, manyadjustments means are incorporated into the grinding assembly. When thediameter of the pin is changed, the center of the grinding arrangementmust be adjusted in the direction defined by arrow 189. This adjustmentis accomplished by loosening the fasteners 190 between the base plateand the mounting plate, turning adjustment screws 192 in conjunctionthereby repositioning the center of the grinding arrangement, andretightening the fasteners 190 between the base plate and the mountingplate. The mounting plate has an aperture 191 (also FIG. 3) with agreater diameter than the drum shaft 157 that passes therethroughallowing the mounting plate to slide relative to the drum assembly.

It is also necessary to adjust the angles of the grinders in thegrinding arrangement to accommodate different pin diameters. To thisend, a band 194 is placed around the pivot bases 180. The band passesthrough tunnels 195 in the bearing supports 166, 168. By simultaneouslyturning the band adjustment screws 196 which engage a fixed pin 198 theangles of all the grinders are adjusted simultaneously. Referring toFIGS. 14, 15, and 16, the angles of individual grinders are adjusted byloosening a band attachment screw 200 corresponding to the grinder to beadjusted, and simultaneously turning the pivot base adjustment screws202 of the individual pivot base adjustment mechanism 203 which iswelded to the band 194. The pivot base adjustment screws engage a pin205 which is fixed in the pivot base to adjust the angles of the pivotbase and grinder. The band attachment screw 200 is then retightened tosecure the adjustment. Whether adjusting all of the pivot bases or justone, the angles of the pivot bases and grinders are adjusted about fixedpivot pins 204.

The individual grinders may also be adjusted in a directionperpendicular to their longitudinal axis 206. Referring to FIGS. 17 and18, a grinder adjustment screw 208 is threaded into a vertical wall 210of the pivot base 180. The end of the grinder adjustment screw is fixedinside of a wall 212 of a saddle block 214 with a metal ball 216 forcedinto a groove 218 of the adjustment screw by threaded member 220. Tokeep the saddle block in position relative to the grinder adjustmentscrew, spring washer 221 engages a shoulder 223 of the grinderadjustment screw and the wall 212. By loosening the clamping screw 222the adjustment screw 208 is free to be threaded in and out of thevertical wall of the pivoting base. Thus, the grinder may be adjusted ina direction perpendicular to its longitudinal axis within the verticalwalls of the pivot base.

B. Grinder Assembly

Referring to FIGS. 14 and 19, it is occasionally necessary to change thegrinding wheels of the grinder. To this end, the grinder assembly isprovided with a tilt up feature by which the grinder is tilted upwardly60° as shown in phantom lines 225 in FIG. 19. To tilt the grinder, theclamping screw 222 and a friction clamping screw 227 are loosened. Thesaddle block and grinder pivot upward around pivot pin 224 andadjustment screw 208. The ball and groove arrangement of the adjustmentscrew allows the saddle block to pivot within the vertical wall of thepivot base because the ball bearing rolls in the groove of theadjustment screw. The saddle block is loosened from the pivot basesimply by loosening two bolts 225 corresponding to handles 226 on eachside of the saddle block.

Referring additionally to FIG. 20, the grinder is held between thesaddle block 214 and a saddle clamp 228. Plastic members 230 in thesaddle clamp cushion the grinder inside the saddle block and saddleclamp. By loosening the bolts 232 attaching the saddle clamp to thesaddle block, the grinder may be adjusted longitudinally as illustratedby phantom lines 234.

VI. The Pins

The pins which are a product of this process are shown in FIGS. 21 and22. The flute that has been ground into the threads of the pin has a runout area 236. The run out area is located at the end of the flutetowards the head of the pin and is created because of the circulargrinding wheels. The run out in no way interferes with the function ofthe fastener. As FIG. 22 illustrates, the fastener produced by thepresent process functions similar to the fasteners disclosed in theStencel patents cited herein. The head 250 of the fastener 55 engages aplate 252 and the shaft 254 of the pin extends through apertures in theplate 252 and a second plate 256. The external threads 258 of the pinare engaged by the internal threads 260 of the collar 262. A fasteningtool (not shown) engages the semicircular convex lobes 264 to tightenthe collar onto the pin. At the desired amount of torque, the fasteningtool plastically deforms the lobes pushing material inwardly into theflutes 266 thereby securing the collar to the pin and providing adesired axial load. The pin is held from rotation during the tighteningprocess by utilizing the wrenching surfaces 268 internally located atthe threaded end of the pin 55.

VII. Operation of Machine for the Mass Production of Pins

In operation, the five spindle fluting machine disclosed is capable ofthe mass production of the pin of the described fastener. Largequantities of threaded pin blanks are loaded into the feed bowl in anyorientation. The feed bowl properly orients the threaded pin blanks andtransfers them to the feed track. The feed track becomes filled withthreaded pin blanks over its entire length and remains filled if thefeed bowl is supplied with pins. During rotation of the drum assembly,the threaded pin blanks in the feed track slide against the shell untilthe aperture of the insert blank is properly aligned with the feedtrack. A first pin, aided by gravity acting on the pin and the otherpins pushing thereon, is loaded into the aperture of the insert blank ofa first hold down assembly. The drum assembly then rotates throughone-quarter arc until the first hold down assembly is at the grindstation and a second hold down assembly is at the feed station. Whilethe drum assembly is temporarily stopped, the first pin is ground whilea second pin is simultaneously loaded into the second hold downassembly. The drum assembly then rotates again until a third hold downassembly is at the feed station, the second hold down assembly is at thegrind station, and the first hold down assembly is at the eject station.Simultaneously, a third pin is fed into the third hold down assembly,the second pin in the second hold down assembly is fluted, and the firstpin falls out of the first hold down assembly aided only by gravity. Thedrum assembly is again rotated, and if the first pin was not ejected bygravity, the ejection arm will extend outward and eject the pin into thechute. Thus the ejection arm assures that the pin is ejected. The drumassembly stops rotating when a fourth hold down assembly is at the feedstation, the third hold down assembly is at the grind station, thesecond hold down assembly is at the eject station, and the first holddown assembly is at the idle station. Again substantiallysimultaneously, a fourth pin is inserted into the fourth hold downassembly, the third pin in the third hold down assembly is ground, andthe second pin falls from the second hold down assembly. The drumassembly rotates until first hold down assembly is again at the feedstation. This process is continuously repeated providing the massproduction of the pin of the fastener.

Thus, a fluting machine is disclosed which utilizes a circulararrangement of grinders to more efficiently manufacture self lockingfasteners which provide set axial loads. While embodiments andapplications of this invention have been shown and described, it isapparent to those skilled in the art that many more modifications arepossible without departing from the inventive concepts herein. It is,therefore, to be understood that within the scope of the appendedclaims, this invention may be practiced otherwise than as specificallydescribed.

What is claimed is:
 1. A threaded pin fastener having a plurality offlutes fabricated by first forming threads on the pin and thensimultaneously grinding flutes on the pin.
 2. The fastener of claim 1wherein the pin includes a shank and a head positioned at one end of theshank.
 3. The fastener of claim 1 wherein the threads are on an outersurface of the shank beginning at an end of the shank opposite the head.4. The fastener of claim 3 wherein the flutes are positioned on thethreaded end of the shank.
 5. The fastener of claim 4 wherein the fluteincludes a run out portion extending towards the head of the pin.
 6. Thefastener of claim 5 wherein the shank includes a wrenching surfaceinternally located at the threaded end of the shank.
 7. The fastener ofclaim 2 further comprising a collar for receipt on the shank oppositethe head.
 8. The fastener of claim 7 wherein the collar is internallythreaded and includes semicircular convex lobes located on an externalsurface of the collar.
 9. The fastener of claim 8 wherein the convexlobes plastically deform into the flutes upon torque applied to thecollar.